EP0670979A4 - Shock absorbing means for flow control devices. - Google Patents
Shock absorbing means for flow control devices.Info
- Publication number
- EP0670979A4 EP0670979A4 EP19920904727 EP92904727A EP0670979A4 EP 0670979 A4 EP0670979 A4 EP 0670979A4 EP 19920904727 EP19920904727 EP 19920904727 EP 92904727 A EP92904727 A EP 92904727A EP 0670979 A4 EP0670979 A4 EP 0670979A4
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- seat ring
- ring
- connecting member
- seat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000035939 shock Effects 0.000 title abstract description 20
- 239000012530 fluid Substances 0.000 claims description 17
- 238000007789 sealing Methods 0.000 claims description 13
- 238000004873 anchoring Methods 0.000 claims description 7
- 230000005484 gravity Effects 0.000 claims description 7
- ZPEZUAAEBBHXBT-WCCKRBBISA-N (2s)-2-amino-3-methylbutanoic acid;2-amino-3-methylbutanoic acid Chemical compound CC(C)C(N)C(O)=O.CC(C)[C@H](N)C(O)=O ZPEZUAAEBBHXBT-WCCKRBBISA-N 0.000 claims description 2
- 238000010276 construction Methods 0.000 claims description 2
- 230000000694 effects Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 abstract description 7
- 239000006096 absorbing agent Substances 0.000 abstract 1
- 239000000463 material Substances 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000006978 adaptation Effects 0.000 description 2
- 239000012634 fragment Substances 0.000 description 2
- 230000003116 impacting effect Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 102000012152 Securin Human genes 0.000 description 1
- 108010061477 Securin Proteins 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- NQLVQOSNDJXLKG-UHFFFAOYSA-N prosulfocarb Chemical compound CCCN(CCC)C(=O)SCC1=CC=CC=C1 NQLVQOSNDJXLKG-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K25/00—Details relating to contact between valve members and seats
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K47/00—Means in valves for absorbing fluid energy
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0433—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with vibration preventing means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
- F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
- F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
- F16K17/0466—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with a special seating surface
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S137/00—Fluid handling
- Y10S137/904—Cushion check valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7738—Pop valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7758—Pilot or servo controlled
- Y10T137/7762—Fluid pressure type
Definitions
- This invention relates to shock absorbing means for flow control devices, a more particularly to shock absorbing means for reciprocable flow control membe of flow control devices such as valves.
- shock absorbing sealing means for flow control devices such as valve have utilized elastomeric members for absorbing shock.
- U.S. Pate No. 4,858,642 dated August 22, 1989 shows a pressure operated relief valve i which an elastomeric member is positioned between a valve disc and a disc hold to absorb shock forces upon reseating of the valve member resulting from reduction in pressure after actuation of the valve member.
- Elastomeric members ar subject to deterioration at high temperatures, such as temperatures over around 50 F for example.
- Prior application serial no. 502,047 filed March 30, 1990 shows a sh absorbing sealing means for reciprocable flow control members of flow cont devices such as valves.
- the specific embodiments illustrated in application serial 502,047 are directed to such shock absorbing means in which the shock absorbi member is mounted on and carried by the reciprocable valve member with t shock absorbing member flexing or deflecting upon contact of the valve mem with a fixed seat ring thereby to absorb the impact forces.
- the present invention provides a shock absorbing sealing means reciprocable flow control members, such as valves, in which the shock absorbi member is mounted on the annular seat or nozzle against which the reciproca flow control member seats.
- the reciprocable flow control member norma comprises a reciprocable valve member in a pressure relief valve, for example, a upon unseating of the valve member at a predetermined high fluid pressure, t valve member oftentimes reseats with an impact force exerted against the seat. minimize wear, damage, leakage, and the like to impacting members, it is desira that the impact forces or energy generated by impact be dissipated or absorb with minimal radial deflection between contacting faces of the seat ring a reciprocable valve member.
- the seat assembly of the present invention defines nozzle or seat ring extending about a flow passage and a flexible connecti member extends outwardly from the seat ring to means anchoring the seat ring.
- T flexible connecting member permits by flexure thereof upon impact of the val member against the seat ring a cushioned longitudinal movement of the reciprocabl valve member after contact with the metal seat ring thereby to absorb impact force Bending movements are exerted at the hinging or joining of opposite ends of th flexible connecting member between the anchoring means and the metal seal rin of the seat assembly.
- the size of the flexible connecting member and the se ring may be determined depending on the specifications and operating parameter for the valve structure. It is an object of this invention to provide shock absorbing means for a hi temperature flow control device having a reciprocable flow control member mova along a longitudinal axis and seating against a flexible seat ring.
- An additional object of this invention is to provide shock absorbing means a safety relief valve seated in closed position on a nozzle about the flow passa with a generally radially extending flexible member connected to the nozzle absorbing impact forces upon impact of the relief valve member against the nozz
- Figure 1 is a schematic view of a safety relief system illustrating a main rel valve and associated pilot valve positioned on a pressure vessel for utilizing t present invention
- Figure 2 is an enlarged cross section of the pilot operated pressure relief val shown in Figure 1 with the reciprocable valve member shown in an open positi to permit fluid flow through the valve for relieving fluid pressure and adapted reseating against the nozzle ring about the flow passage;
- Figure 3 is an enlarged fragment of Figure 2 illustrating particularly the sizi of the members forming the shock absorbing sealing means of the present inventi and showing in broken lines the movement of the nozzle ring upon flexing of t flexible member connected to the nozzle ring after impact of the valve memb against the nozzle ring;
- Figure 4 is a cross section of another embodiment of the present inventi showing a non-pilot operated pressure relief valve in closed position seated on t flexible nozzle assembly of the present invention.
- FIG. 5 is an enlarged fragment of Figure 4 showing the shock absorbi sealing means of the present invention.
- FIG. 1 a pressure vessel or tank is shown generally at having an outlet 12 extending therefrom.
- a main relief valve is indicated generally
- a pilot val generally indicated at 20 is mounted on relief valve 14.
- An inlet line 22 extends fro main valve 14 to pilot valve 20 and an outlet line 24 extends from pilot valve 20 the downstream side of body 16.
- a control fluid line 26 extends from pilot valve to a dome or dome chamber 28 of main relief valve 14.
- the pressure release syste illustrated is particularly adapted for high temperature over around 350 F and m be utilized with steam, liquid, or vapor with various types of pressure vessels or flu flow lines extending to main relief valve 14.
- An exhaust 29 provides a vent atmosphere for pilot valve 20.
- Valve body 16 defines an inlet flow passage at 30 and an outlet flow passa at 32.
- a fluid operated reciprocable valve member is generally indicated at 34 havi dome chamber 28 therein and mounted for reciprocable movement between op and closed positions.
- Valve member 34 moves to an open position as shown i Figure 2 resulting from a predetermined high fluid pressure being reached i pressure vessel 10 and inlet passage 30 sensed by pilot line 22.
- pilot line 22 Upon a reductio in fluid pressure in pressure vessel 10 and inlet passage 30 as sensed by pilot valv 20, valve member 34 reseats on nozzle assembly 38.
- valve member 3 moves rapidly to closed seated position to exert impact forces against nozzl assembly 38.
- a nozzle assembly or seat ring assembly generally indicated at 38 forms a important part of this invention and is mounted about flow passage 32.
- Nozzl assembly 38 includes an inner nozzle or seat ring indicated at 40, an outer securin or anchoring ring indicated at 42, and a flexible connecting member 44 extendin in a generally radial direction between seat ring 40 and anchor ring 42.
- a sleeve generally indicated at 45 has an inn periphery 46 defining flow passage 32 and a threaded outer periphery 48.
- the inn annular end 50 of sleeve 45 has an annular recess defining a shoulder 52 and outer peripheral surface 54.
- Body 16 is internally threaded at 55 and has an inn flange or overhanging lip 56 spaced in opposed relation to annular end 50 to defi a receiving groove therebetween.
- Anchor ring 42 of nozzle assembly 38 h opposed ends 58 and sealing gaskets 60 which are gripped between lip 56 and e 50 upon threading of sleeve 45 within body 16 tightly against anchor ring 42.
- Nozzle or seat ring 40 has an inner peripheral surface 62 and an out peripheral surface 64 which are spaced radially from each other. The center gravity of seat ring 40 is shown at 65.
- the upper annular end 66 of seat ring defines a seating face having a width W2 for contacting and sealing against face of valve member 34 which has a width T1.
- the lower annular end 68 of seat ring is received within the inner recess of sleeve 45 and may contact shoulder 52 restrict axial movement of ring 40 and overstressing of seat assembly 38 up impact loads from valve member 34 as will be explained further below.
- Flexible connecting member 44 extends in a generally radial direction betwe seat ring 40 and anchor ring 42. Connecting member 44 is hinged to the inn peripheral surface of outer ring 42 about point 72 and hinged to the outer periphe surface 64 of seat ring 40 at point 74. Flexible connecting member 44 flexes aft initial contact of sealing face 36 on valve member 34 with face 66 of seat ring 40 a is constructed and arranged for a predetermined flexure relative to anchor ring for absorbing impact forces with minimal radial and angular deflections of seali face 66 on seat ring 40 and for providing alignment between faces 36 and 66.
- seat ring 40 of nozzle assembly 38 moves an axi distance D after contact of seal face 36 with seat face 66.
- Distance D is at lea greater than around .002 inch and may be as high as around .030 inch or great depending primarily on such factors as the size of valve member 34 and vario operating parameters.
- Planar rear face 68 of seat ring 40 is normally spaced fro shoulder 52 and shoulder 52 acts as a stop when contacted by rear face 68 to li the maximum travel S of seat ring 40 past the elastic limit of connecting member after seat face 66 is contacted by seal face 36.
- the longitudinal axis of flexib connecting member 44 is shown at 76.
- the thickness of connecting member 4 indicated at T.
- Seat ring 40 has a maximum thickness indicated at T2, and a width indicat at W.
- the center of gravity of seat ring 40 indicated at 65 is offset an axial dista D1 from the centerline of connecting member 44 at hinge point 72 in a directi toward or longitudinally inwardly of seat face 66.
- Such an offset has been fou desirable in order to minimize any angular or radial deflection of seat face 66 up flexing of connecting member 44 resulting from movement of seat ring 40 after s face 36 contacts seat face 66.
- An offset distance D1 of at least around .050 inch believed desirable in order to minimize the deflection of seat face 66 to insignificant amount.
- the maximum thickness T1 of seat ring 40 be at le around twice the thickness T of connecting member 44. Further, it is desirable th the width W of seat ring 40 be at least around three times the thickness T connecting member 44. Additionally, in order to minimize the angular and rad deflections of face 66 upon flexure of connecting member 44, the longitudinal a
- connecting member 44 slopes toward the center of gravity 65 from hinge poi 72 at the inner peripheral surface of outer ring 42 at a positive slope angle sho at angle A in Figure 3. It is believed that angle A should be between around one-h degree and ten degrees in order to obtain optimum results. It is noted that t center of gravity 65 is positioned between valve member 34 and connecting memb
- connecting member 44 in the embodiment of Figures 1-3. It is to be understood that in the eve connecting member 44 is positioned between valve member 34 and the center gravity, connecting member 44 will slope in an opposite direction at a negative slo angle.
- Planar face 36 is of a width T1 greater than the width W2 of planar face 66 f the most effective sealing action and with minimal radial and angular deflection occurring after contact. Such an arrangement accommodates any lack concentricity between faces 36 and 66.
- Seal face 36 is formed of a harder fac material than is seat face 66. It is apparent from the above that the design of the flexible connecting memb 44 between seat ring 40 and anchor ring 42 may be predetermined in order to ha sufficient flexure to absorb the impact forces while minimizing the deflection of se face 66. While anchor ring 42, connecting member 44, and seat ring 40 are sho as an integral construction in seat assembly 38, it is to be understood th connecting member 44 may be formed of a separate member, if desired, such a Belleville washer, for example.
- Pressure relief valve 14A has a valve body 16A including an inlet flow passage 3 and an outlet flow passage 32A.
- a reciprocable valve member 34A has an annul seal face 36A and is urged into seating engagement by spring 37A.
- Improved nozzle assembly 38A has an upper annular seat face 66A engagi seal face 36A on valve member 34A.
- Nozzle assembly 38A includes an inner se ring 40A, an outer anchor ring 42A, and a flexible connecting member 4 extending in a generally radial direction between the outer periphery 64A of seat ri 40A and the inner periphery of anchor ring 42A.
- valve member 34A and seal fa 36A are forced outwardly against the bias of spring 37A to permit fluid flow throu fluid passage 32A.
- valve memb 34A under the bias of spring 37A moves nozzle assembly 38A to a reseated positi on seat face 60A of seat ring 40A on nozzle assembly 38A.
- Flexible connecting member or web 44A functions in the same manner as t embodiment of Figures 1-3 and is generally identical to the embodiment of Figur 1-3.
- the longitudinal axis 76A of connecting member 44A has a positive slo shown at angle A between hinge points 72A and 74A.
- Angle A is generally equal angle A in the embodiment of Figures 1-3 and slopes downwardly from seat ri 40A toward anchor ring 42A as in the embodiment of Figures 1-3.
- the cen of gravity 65A of seat member 40A is positioned forwardly of hinge point 72A tow face 66A as shown at D1.
- Distance D1 is generally identical to the distance D1 in t embodiment shown in Figures 1-3 thereby to minimize the deflection of face 6 resulting from the flexing of connecting member 44A.
- Seat ring 40A moves distance D as in the embodiment of Figures 1-3 and rear face 68A of seat ring 4 engages shoulder 52A in abutting contact to limit the movement of seat ring 4 past the elastic limit of connecting member 44A.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Safety Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US643485 | 1991-01-22 | ||
US07/643,485 US5064169A (en) | 1990-03-30 | 1991-01-22 | Shock absorbing means for flow control devices |
PCT/US1992/000525 WO1992013222A1 (en) | 1991-01-22 | 1992-01-22 | Shock absorbing means for flow control devices |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0670979A4 true EP0670979A4 (en) | 1994-06-01 |
EP0670979A1 EP0670979A1 (en) | 1995-09-13 |
EP0670979B1 EP0670979B1 (en) | 1998-03-25 |
Family
ID=24581019
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92904727A Expired - Lifetime EP0670979B1 (en) | 1991-01-22 | 1992-01-22 | Shock absorbing means for flow control devices |
Country Status (7)
Country | Link |
---|---|
US (1) | US5064169A (en) |
EP (1) | EP0670979B1 (en) |
JP (1) | JP3175833B2 (en) |
KR (1) | KR100192853B1 (en) |
CA (1) | CA2088508C (en) |
DE (1) | DE69224916T2 (en) |
WO (1) | WO1992013222A1 (en) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5307831A (en) * | 1992-06-29 | 1994-05-03 | Keystone International Holdings Corp. | Safety relief valve for pressure vessels |
FR2705130B1 (en) * | 1993-05-12 | 1995-06-23 | Snecma | FLUID DISTRIBUTION BODY WITH SELF-CENTERING SEAT. |
DE19730276A1 (en) * | 1997-07-15 | 1999-01-21 | Wabco Gmbh | Device with at least two parts movable relative to each other |
JP2001082625A (en) * | 1999-09-13 | 2001-03-30 | Denso Corp | Solenoid valve |
DE20006775U1 (en) | 2000-04-12 | 2000-08-10 | Xomox International GmbH & Co, 88131 Lindau | Valve |
US8671972B2 (en) * | 2010-09-24 | 2014-03-18 | Mike Winn | Safety valve system for overpressure protection of hydraulic circuits |
CN103671938B (en) * | 2012-09-21 | 2018-02-13 | 艾默生过程管理调节技术公司 | Autoregistration valve port |
DE202014105444U1 (en) * | 2014-11-12 | 2014-11-25 | Ari-Armaturen Albert Richter Gmbh & Co. Kg | safety valve |
US11090713B2 (en) * | 2017-09-29 | 2021-08-17 | Fisher Controls International Llc | Bi-metal valve body casting and method of making same |
CN114144609A (en) * | 2019-07-24 | 2022-03-04 | 艾默生自动化解决方案终控美国公司 | Quick dome loading pilot valve |
US20220196181A1 (en) * | 2020-12-23 | 2022-06-23 | Goodrich Corporation | Inflatable systems with electro-pneumatic valve modules |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE71059C (en) * | CH. S. BAVIER in New-York, V. St. A., 32 Nassaustr | Flange and valve seal | ||
FR2443631A1 (en) * | 1978-12-07 | 1980-07-04 | Zahnradfabrik Friedrichshafen | VALVE, IN PARTICULAR COMPRESSION VALVE FOR PISTON PUMP |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US452357A (en) * | 1891-05-19 | Valve | ||
US820154A (en) * | 1905-07-12 | 1906-05-08 | Nathan P Towne | Valve. |
US1671139A (en) * | 1926-01-25 | 1928-05-29 | Wylie G Wilson | Valve |
US1800127A (en) * | 1926-01-25 | 1931-04-07 | Wilson Rings Company | Valve |
US1671140A (en) * | 1926-01-25 | 1928-05-29 | Wylie G Wilson | Valve |
US1654516A (en) * | 1926-01-25 | 1927-12-27 | Wylie G Wilson | Valve |
US1679779A (en) * | 1926-04-08 | 1928-08-07 | William F Oberhuber | Valve and flanged seal |
US1878222A (en) * | 1927-10-04 | 1932-09-20 | Wylie G Wilson | Valve and the like |
US1847385A (en) * | 1930-05-26 | 1932-03-01 | Dengler Benjamin Franklin | Valve |
US2163472A (en) * | 1936-07-07 | 1939-06-20 | Oil Well Supply Co | Valve |
US2398370A (en) * | 1939-07-31 | 1946-04-16 | Perry H Gentzel | Seat for safety valve constructions |
US2597474A (en) * | 1948-09-23 | 1952-05-20 | William B Griffith | Dry pipe valve |
US2643671A (en) * | 1952-06-21 | 1953-06-30 | Manning Maxwell & Moore Inc | Spring loaded pop-safety valve |
US3063467A (en) * | 1960-04-08 | 1962-11-13 | Mission Mfg Co | Valve seats |
US3430646A (en) * | 1966-11-21 | 1969-03-04 | Bendix Corp | Hot gas relief valve |
GB1164678A (en) * | 1966-12-27 | 1969-09-17 | Toa Valve Company Ltd | Improvements relating to Pop Safety Valves |
US3702141A (en) * | 1971-02-22 | 1972-11-07 | Dresser Ind | Gas type safety valve |
US3785029A (en) * | 1972-08-28 | 1974-01-15 | Gen Motors Corp | Method of assembling inserts with precision looseness |
US4188013A (en) * | 1977-08-08 | 1980-02-12 | Honeywell Inc. | Gas valve seating member |
JPS5551173A (en) * | 1978-10-09 | 1980-04-14 | Toa Valve Kk | Preparation of valve body in safety valve |
SU859738A1 (en) * | 1978-10-17 | 1981-08-30 | Предприятие П/Я А-7899 | Locking pair |
US4858642A (en) * | 1988-01-25 | 1989-08-22 | Dresser Industries, Inc. | Impact resistant pressure relief valve |
-
1991
- 1991-01-22 US US07/643,485 patent/US5064169A/en not_active Expired - Lifetime
-
1992
- 1992-01-22 JP JP50541292A patent/JP3175833B2/en not_active Expired - Lifetime
- 1992-01-22 EP EP92904727A patent/EP0670979B1/en not_active Expired - Lifetime
- 1992-01-22 CA CA002088508A patent/CA2088508C/en not_active Expired - Lifetime
- 1992-01-22 KR KR1019930702009A patent/KR100192853B1/en not_active IP Right Cessation
- 1992-01-22 DE DE69224916T patent/DE69224916T2/en not_active Expired - Lifetime
- 1992-01-22 WO PCT/US1992/000525 patent/WO1992013222A1/en active IP Right Grant
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE71059C (en) * | CH. S. BAVIER in New-York, V. St. A., 32 Nassaustr | Flange and valve seal | ||
FR2443631A1 (en) * | 1978-12-07 | 1980-07-04 | Zahnradfabrik Friedrichshafen | VALVE, IN PARTICULAR COMPRESSION VALVE FOR PISTON PUMP |
Non-Patent Citations (1)
Title |
---|
See also references of WO9213222A1 * |
Also Published As
Publication number | Publication date |
---|---|
CA2088508A1 (en) | 1992-07-23 |
JPH06506284A (en) | 1994-07-14 |
DE69224916T2 (en) | 1998-07-16 |
KR100192853B1 (en) | 1999-06-15 |
CA2088508C (en) | 1999-01-19 |
KR930703564A (en) | 1993-11-30 |
JP3175833B2 (en) | 2001-06-11 |
EP0670979A1 (en) | 1995-09-13 |
EP0670979B1 (en) | 1998-03-25 |
DE69224916D1 (en) | 1998-04-30 |
US5064169A (en) | 1991-11-12 |
WO1992013222A1 (en) | 1992-08-06 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
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